EP0945696A1 - Aluminiumsammler - Google Patents

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Publication number
EP0945696A1
EP0945696A1 EP99302345A EP99302345A EP0945696A1 EP 0945696 A1 EP0945696 A1 EP 0945696A1 EP 99302345 A EP99302345 A EP 99302345A EP 99302345 A EP99302345 A EP 99302345A EP 0945696 A1 EP0945696 A1 EP 0945696A1
Authority
EP
European Patent Office
Prior art keywords
fluid
heat exchanger
passageways
header
headers
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP99302345A
Other languages
English (en)
French (fr)
Inventor
Jr Ivan Woodhull
Rial Hamman
Kenneth Mciver
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KARMAZIN PRODUCTS CORP
Original Assignee
KARMAZIN PRODUCTS CORP
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US09/266,783 external-priority patent/US6161614A/en
Application filed by KARMAZIN PRODUCTS CORP filed Critical KARMAZIN PRODUCTS CORP
Priority to EP99302345A priority Critical patent/EP0945696A1/de
Publication of EP0945696A1 publication Critical patent/EP0945696A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0207—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions the longitudinal or transversal partitions being separate elements attached to header boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/16—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes extruded

Definitions

  • the present invention relates generally to heat exchangers and, more particularly, to such heat exchangers having an aluminum extruded header construction and a temperature responsive by-pass assembly.
  • Heat exchangers of the fin and tube type are employed for cooling or otherwise transferring heat between two fluids. Generally, one of the fluids is circulated internally through conduits provided in the heat exchanger core and the other is passed over the exterior of the conduits and associated heat radiating fins. Such heat exchangers are commonly employed in heavy construction machinery as well as other apparatus for use in cooling oil, hydraulic fluid or the like.
  • the fluid may exert a high level of pressure on the heat exchanger and has the potential for subjecting the heat exchanger to even higher pressure spikes.
  • the pressurized fluid may damage the header portion or core portion of the heat exchanger if either portion is not designed properly.
  • the fluid may have a relatively high viscosity when cool such as at start-up of the equipment and become thinner as it is warmed during use.
  • This high viscosity may cause higher than desired pressure in the inlet header of such heat exchangers due to the viscous resistance of fluid flow through the relatively small passages in the heat exchanger core.
  • the resistance may prevent a sufficient amount of fluid from being circulated through the system which in an extreme case could result in excessive equipment wear.
  • the hereinafter described and illustrated embodiments of heat exchanger include a first extruded aluminum header spaced apart and arranged essentially parallel to a second extruded aluminum header.
  • the first and second headers include a plurality of parallel passageways extending therethrough along a longitudinal axis.
  • the passageways are fluidly interconnected by at least one cross-drilled transverse bore extending essentially perpendicularly to the longitudinal axis.
  • a core assembly is secured between the first and second headers and includes a plurality of restricted fluid conduits and heat radiating fins surrounding the fluid conduits.
  • An optional valved by-pass assembly fluidly communicates with the headers and core assembly while providing an alternate pathway independent thereof.
  • the by-pass assembly is responsive to fluid temperature for directing fluid flow either into or exterior of the heat exchanger core assembly.
  • the present invention is directed towards a heat exchanger suitable for withstanding elevated pressures of the fluid contained therein.
  • the heat exchanger includes a pair of oppositely disposed and spaced apart aluminum extruded headers including a plurality of parallel passageways extending therethrough along a longitudinal axis.
  • the passageways are fluidly interconnected by at least one cross-drilled transverse bore extending essentially perpendicular to the longitudinal axis.
  • An optional by-pass assembly fluidly communicates with the first header while providing an alternate pathway independent thereof.
  • the by-pass assembly includes a temperature responsive by-pass valve. As such, high viscosity and low temperature fluid is allowed to by-pass the core of the heat exchanger thereby reducing the time required for the fluid to reach a normal operating temperature.
  • the heat exchanger 10 includes a first header 12, a second header 14 spaced from the first header 12 and arranged in substantially parallel relationship therewith.
  • a pair of spaced apart frame members 16 and 18 extend therebetween adjacent opposite ends of the first and second headers 12 and 14.
  • a heat exchanger core assembly 20 is disposed between first and second headers 12 and 14 and is in fluid communication therewith.
  • the core assembly includes a plurality of relatively small diameter fluid conduits 22 extending generally perpendicular to the longitudinal axis of the first and second headers 12 and 14.
  • the fluid conduits 22 are surrounded by a plurality of fins 24 extending substantially parallel to the longitudinal axis of the first and second headers 12 and 14.
  • core assembly 20 will be of the stacked fin and tube type such as disclosed in U.S. Patent Nos. 3,430,692 and 3,601,878, the disclosures of which are hereby incorporated by reference.
  • the first header 12 has an inlet opening 26 adjacent one end thereof which is adapted to be connected to a fluid supply line (not shown).
  • the first header 12 has a similar outlet opening 28 adapted to be connected to a discharge line (also not shown).
  • a pair of L-shaped elbow mounting brackets 30 and 32 are fixed by welding or other conventional means to an outboard edge of the second header 14.
  • a pair of mounting brackets 34 and 36 are fixed by welding or other conventional means to an outboard edge of the first header 12.
  • the first and second headers 12 and 14 include three parallel passageways 42 extending essentially parallel to the longitudinal axis of the first and second headers 12 and 14.
  • the passageways 42 fluidly interconnect the inlet opening 26 and outlet opening 28 via the headers 12 and 14 and the core assembly 20.
  • each of the headers 12 and 14 are formed from aluminum through an extrusion process.
  • the extruded aluminum stock having the desired number of longitudinally extending fluid passages 42 is easily cut to the desired length required for the intended heat exchanger and the opposite ends thereof are closed off by welding suitable plates thereto. Because the respective passages 42 are interconnected via bores 50, exchange therebetween at the end plates is not of concern.
  • a two pass heat exchanger such as that shown in FIGS. 1-3
  • two substantially equal lengths of header stock are joined together with a divider plate 44 welded therebetween.
  • divider plate 44 it may be possible to extrude header 12 in such a manner as to form divider plate 44 integrally therewith if desired.
  • the conduits 42 of the first header 12 are divided into supply conduits 46 proximate the inlet opening 26 and discharge conduits 48 proximate the outlet opening 28.
  • each of the passageways 42 of the second header 14 is in fluid communication with an adjacent passageway 42 by way of a transverse bore 50 extending essentially perpendicularly to the longitudinal axis of the second header 14.
  • the transverse bore 50 is formed by cross-drilling the extruded second header 14.
  • the end of the transverse bore 50 at the outboard edge of the second header 14 is sealed by a suitable plug 52 welded in place to prevent leakage of the second header 14.
  • each of the conduits 42 fluidly communicates with a plurality of the fluid conduits 22 arranged perpendicularly thereto and which form a part of the core assembly.
  • each of the fluid conduits 22 includes an inlet 54 bifurcated into a pair of parallel pipes 56 which extend through the core assembly 20 to the first header 12 (see FIG. 1).
  • the pair of parallel pipes 56 reconverge at an opposite end into a single outlet 58 (FIG. 1) communicating with the first header 12.
  • the terms inlet and outlet as used herein are inter-changeable and are merely indicative of the direction of fluid flow. In the embodiment illustrated in FIG.
  • the plane defined by the pair of parallel pipes 56 is parallel to the frame members 16 and 18 thereby allowing inclusion of a greater number of flow paths between the two headers for a given envelope size. As such, a short and wide heat exchanger may be provided while still providing significant surface area for heat exchange.
  • fluid such as oil is supplied to the inlet opening 26 via a supply line and enters into the supply passageways 46 of the first header 12.
  • the fluid Upon the fluid entering the first of the supply passageways 46 (i.e., the passageway 46 communicating with inlet opening 26) the fluid fills the remaining supply passageways 46 in the first header 12 by propagating through one or more transverse bores 50.
  • This propagation can be controlled (i.e., enhanced or reduced) by changing the diameter and/or number of transverse bores 50 provided therein, although it is preferred to incorporate a sufficient number and/or sufficiently large diameter bores to insure substantially free flow between and equal pressure in each of the passages 42.
  • the fluid propagates through the fluid conduits 22 in communication therewith to the second header 14.
  • the fluid fills passageways 42 formed therein via the transverse bore 50.
  • the fluid then propagates from the second header 14, through the remaining fluid conduits 22 to the discharge passageways 48 formed in the first header 12.
  • the fluid is discharged from the heat exchanger 10 through the outlet opening 28 and a discharge line coupled therewith.
  • the fluid traverses the conduits 22 of the core assembly 20, its temperature is reduced as heat is conducted and convected from the fluid to the walls of the conduits 22 and to the fins 24.
  • heat exchanger 10 as illustrated and described is a two pass heat exchanger (i.e., the fluid flows through the core twice).
  • heat exchanger 10 may be easily fabricated as a single pass heat exchanger by merely deleting divider 44 from header 12 and moving the outlet fitting 28 to the other header 14.
  • a multiple pass heat exchanger may be easily fabricated by providing any number of dividers 44 appropriately positioned in each of headers 12 and 14.
  • FIG. 6 an alternate embodiment of the present invention is illustrated.
  • This embodiment is substantially similar to the embodiment depicted in FIGS. 1-5 with the exception that the plurality of fluid conduits 22a including the pairs of parallel pipes 56a have been rotated by 90° relative to horizontal such that the plane defined by the pair of parallel pipes 56a is perpendicular to the frame members 16a and 18a.
  • This arrangement is preferred, as it enables the longitudinal spacing between openings 22 to be increased.
  • the inlet opening 26, outlet opening 28 and the by-pass openings 38 and 40 of the first embodiment have been combined into a by-pass valve assembly 58.
  • the by-pass valve 58 is operable for directing fluid flow into or independent of the heat exchanger 10a in response to either the pressure or temperature of the fluid, or both.
  • the temperature and pressure responsive by-pass valve assembly 58 includes a by-pass valve inlet 60 fluidly communicating with the inlet opening 26a and a valve chamber 62.
  • the by-pass valve assembly 58 includes a by-pass valve outlet 64 fluidly communicating with the outlet opening 28a and the valve chamber 62.
  • a thermally responsive valve 65 is disposed within the valve chamber 62 and includes a valve member 66 operable to open and close the passageway defined between the inlet 60 and outlet 64.
  • the valve 65 is preferably of the type which includes a wax motor operable to drive the valve member 66 into a position such that communication between inlet 60 and outlet 64 via valve chamber 62 is prevented when the fluid exceeds a predetermined temperature.
  • valve 65 may include a biasing spring operable to resiliently bias valve member 66 into a closed position but allow communication between inlet 60 and outlet 64 via chamber 62 when valve member 66 is moved into an open position in response to an increase in the differential pressure between inlet 60 and outlet 64 above a predetermined level.
  • the by-pass valve 65 when the by-pass valve 65 is closed, i.e., the valve member 66 engages the valve seat, the fluid travels through the by-pass valve inlet 60 and into the inlet opening 26a. After passing through the first header 12, core assembly 20, second header 14 and returning to the first header 12, the fluid propagates through the outlet opening 28a and exits the by-pass valve outlet 64 to a discharge line. Thus, when the fluid is insufficiently warm (and thus too viscous) it may be directed away from the heat exchanger 10.
  • first header 12b an alternate embodiment header, such as first header 12b, is illustrated.
  • first header 12b is illustrated, it can be appreciated that the second header 14 could readily substitute therefore.
  • the first header 12b includes two enlarged diameter parallel passageways 42b extending therethrough along the longitudinal axis.
  • the passageways 42b communicate with conduits 22b and are interconnected by a transverse bore 50b which is sealed with a suitable plug 52b. Accordingly to this embodiment, a more narrow header 12b is provided.
  • a header such as first header 12c, includes six relatively smaller diameter parallel passageways 42c extending therethrough along the longitudinal axis.
  • the passageways 42c are fluidly interconnected by a transverse bore 50c sealed at an outboard edge of the header 12c with a suitable plug 52c.
  • the passageways 42c also communicate with the conduits 22c.
  • the embodiments illustrated in FIGS. 5, 8 and 9 demonstrate that the number and diameter of passageways 42c in the header 12c can be controlled by a designer according to the particular needs of the application into which the present invention is incorporated, such as, fluid viscosity, and available space as well as required cooling capacity.
  • the embodiment illustrated in FIG. 9 is well suited for use in a wide but, perhaps, short space.
  • heat exchanger 70 is a two pass heat exchanger, is generally similar to heat exchangers 10 and 10a described above, and includes a core assembly 72 preferably of the stacked fin and tube type having a pair of headers secured to opposite ends thereof (only the inlet/outlet header 74 being shown). Header 74 and the return header (not shown) are of the extruded construction described above, with header 74 being substantially identical to header 12a except for the positioning and manner of attachment of the by-pass valve assembly 76 and the location of the inlet and outlet openings provided therein.
  • inlet and outlet openings 78 and 80 are provided in close proximity to each other in the sidewall portion 82 of header 74.
  • a plate member 84 is secured to sidewall portion 82 and includes a pair of spaced openings 85, 87 therein which are positioned in aligned relationship to respective inlet and outlet openings 78 and 80.
  • plate member 84 will be secured to sidewall portion 82 so as to form a fluid-tight connection therewith such as by welding although other suitable means for securing plate 84 thereto may be utilized.
  • By-pass valve assembly 76 is generally similar to by-pass valve assembly 58 and includes a housing 86 having an inlet passage 88 which opens into a valve chamber 90 provided in housing 86.
  • a transversely extending passage 92 intersects inlet passage 88 and opens at its inner end to a laterally extending passage 94 which in turn opens outwardly of housing 86 in a position so as to be aligned with opening 85 in plate member 84 when housing 86 is secured thereto.
  • An outlet opening 96 is also provided extending inwardly in substantially parallel spaced relationship to inlet passage 92 and opening at its inner end into a transversely extending passage 98.
  • Transversely extending passage 98 extends through valve chamber 90 and has its outer end sealed by means of a suitable plug 100.
  • transversely extending passage 92 is also sealed by means of a suitable plug 102.
  • a laterally extending passage 104 extends in parallel spaced relationship to laterally extending passage 94 from transversely extending passage 98 and opens outwardly of housing 86 in a position so as to be aligned with opening 87 in plate member 84 when housing 86 is secured thereto.
  • a valve member 106 is removably secured in housing 86 and extends into valve chamber 90.
  • Valve member 106 includes a valve element 108 engageable with a valve seat 110 positioned at the juncture between inlet passage 88 and valve chamber 90 to prevent fluid communication between inlet passage 88 and valve chamber 90.
  • valve member 106 will be substantially identical to valve 65 disclosed above and will include a wax motor operative to move valve element between open and closed positions in response to the temperature of the fluid flowing through heat exchanger 70.
  • Housing 86 is preferably removably secured to plate member 84 by means of a plurality of threaded fasteners 112, 114 and 116. Suitable O-rings may be utilized at the juncture of passages 94 and 104 with passage 87 and 85 in plate member 84 so as to ensure a secure fluid-tight sealing relationship therebetween.
  • a fluid supply line is connected to inlet opening 88 and a fluid discharge line is connected to outlet opening 96.
  • the wax motor of valve member 106 will have operated to move valve element 108 off seat 110 thereby enabling fluid to flow directly from inlet 88 to outlet 96 via valve chamber 90 thus bypassing the core assembly 72.
  • valve member 106 will begin to close thereby increasing the restriction on flow through valve chamber 90 which will result in increasing volume of fluid being directed through heat exchanger core 72. Once the temperature of fluid has increased to the desired operating level, valve 106 will fully close thereby directing all fluid flow through the heat exchanger core.
  • valve 106 The wax motor of valve 106 is positioned so as to be able to continuously sense the temperature of fluid as it leaves the heat exchanger core and thus should for some reason the temperature thereof decrease below the desired level, valve element 108 will be opened again to enable some fluid to bypass the core assembly thus reducing the cooling thereof. It should be noted that valve member 106 may also operate to provide a pressure responsive bypass feature as well. Thus should, for some reason, the pressure drop through the core assembly as sensed between the inlet and outlet rise above a predetermined level, this pressure differential will operate to open valve element 108 to allow fluid to bypass the core assembly thus enabling continued operation of the equipment.
  • FIGS. 10-17 has been shown and described utilizing a header having three fluid passages, headers having a greater or less number of fluid passages may be easily substituted therefor.
  • valve housing 86 may be easily removed by removing the retaining fasteners 112, 114, 116. Thereafter, a second plate having suitable openings for connection of the inlet and outlet fluid lines can be substituted for the valve housing 86 and the equipment then operated without the by-pass feature.
  • valve member 106 malfunction, the entire assembly can be easily replaced or should a replacement valve member not be available, a suitable second plate without the by-pass arrangement can be installed in place thereof.
  • the modular valve housing arrangement described above may facilitate fabrication of the heat exchanger in that the entire heat exchanger can be assembled and subject to an oven brazing process to ensure a fluid-tight seal between the various components after which the valve assembly can be easily assembled thereto.
  • the present inveniton provides a heat exchanger including aluminum extruded headers having a plurality of parallel passageways extending therethrough along a longitudinal axis.
  • the parallel passageways are fluidly interconnected by a transverse bore cross-drilled through the header.
  • a by-pass valve outboard of the heat exchanger provides a fluid passageway independent of the heat exchanger core assembly.
  • the by-pass valve is responsive to the temperature and pressure of the fluid traveling therethrough.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP99302345A 1998-03-27 1999-03-26 Aluminiumsammler Withdrawn EP0945696A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP99302345A EP0945696A1 (de) 1998-03-27 1999-03-26 Aluminiumsammler

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US4974298A 1998-03-27 1998-03-27
US49742 1998-03-27
US09/266,783 US6161614A (en) 1998-03-27 1999-03-12 Aluminum header construction
US266783 1999-03-12
EP99302345A EP0945696A1 (de) 1998-03-27 1999-03-26 Aluminiumsammler

Publications (1)

Publication Number Publication Date
EP0945696A1 true EP0945696A1 (de) 1999-09-29

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EP99302345A Withdrawn EP0945696A1 (de) 1998-03-27 1999-03-26 Aluminiumsammler

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EP (1) EP0945696A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005064259A1 (en) * 2003-12-31 2005-07-14 Giannoni S.P.A. Heat exchanger for water-heating apparatuses
WO2023106857A1 (ko) * 2021-12-10 2023-06-15 한온시스템 주식회사 열교환기 및 상기 열교환기에 사용되는 우회밸브
WO2024005335A1 (ko) * 2022-06-30 2024-01-04 한온시스템 주식회사 열교환기

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB993716A (en) * 1961-05-12 1965-06-02 Babcock & Wilcox Ltd Improvements in or relating to tubular heat exchangers
US3430692A (en) 1967-06-16 1969-03-04 John Karmazin Return bend construction for heat exchangers
US3601878A (en) 1967-06-23 1971-08-31 John Karmazin Method for fabricating a heat exchanger
US4337737A (en) * 1980-05-09 1982-07-06 Murray Pechner Temperature regulator for oil cooling system
EP0442646A2 (de) * 1990-02-12 1991-08-21 Modine Manufacturing Company Vielzug-Verdampfer
DE4232366A1 (de) * 1991-07-11 1994-03-31 Laengerer & Reich Gmbh & Co Ölkühler
EP0608439A1 (de) * 1988-01-28 1994-08-03 Modine Manufacturing Company Verdampfer mit Kondensatansammlung
DE4305060A1 (de) * 1993-02-19 1994-08-25 Behr Gmbh & Co Gelöteter Wärmetauscher, insbesondere Verdampfer
WO1998051983A1 (en) * 1997-05-12 1998-11-19 Norsk Hydro Asa Heat exchanger

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB993716A (en) * 1961-05-12 1965-06-02 Babcock & Wilcox Ltd Improvements in or relating to tubular heat exchangers
US3430692A (en) 1967-06-16 1969-03-04 John Karmazin Return bend construction for heat exchangers
US3601878A (en) 1967-06-23 1971-08-31 John Karmazin Method for fabricating a heat exchanger
US4337737A (en) * 1980-05-09 1982-07-06 Murray Pechner Temperature regulator for oil cooling system
EP0608439A1 (de) * 1988-01-28 1994-08-03 Modine Manufacturing Company Verdampfer mit Kondensatansammlung
EP0442646A2 (de) * 1990-02-12 1991-08-21 Modine Manufacturing Company Vielzug-Verdampfer
DE4232366A1 (de) * 1991-07-11 1994-03-31 Laengerer & Reich Gmbh & Co Ölkühler
DE4305060A1 (de) * 1993-02-19 1994-08-25 Behr Gmbh & Co Gelöteter Wärmetauscher, insbesondere Verdampfer
WO1998051983A1 (en) * 1997-05-12 1998-11-19 Norsk Hydro Asa Heat exchanger

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005064259A1 (en) * 2003-12-31 2005-07-14 Giannoni S.P.A. Heat exchanger for water-heating apparatuses
WO2023106857A1 (ko) * 2021-12-10 2023-06-15 한온시스템 주식회사 열교환기 및 상기 열교환기에 사용되는 우회밸브
WO2024005335A1 (ko) * 2022-06-30 2024-01-04 한온시스템 주식회사 열교환기

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